EP1632685B1 - Zylindrisches rollenlager - Google Patents

Zylindrisches rollenlager Download PDF

Info

Publication number
EP1632685B1
EP1632685B1 EP04733675.5A EP04733675A EP1632685B1 EP 1632685 B1 EP1632685 B1 EP 1632685B1 EP 04733675 A EP04733675 A EP 04733675A EP 1632685 B1 EP1632685 B1 EP 1632685B1
Authority
EP
European Patent Office
Prior art keywords
cylindrical roller
roller
face
cylindrical
flange
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP04733675.5A
Other languages
English (en)
French (fr)
Other versions
EP1632685A4 (de
EP1632685A1 (de
Inventor
Hiromichi c/o NSK LTD. TAKEMURA
Masanao c/o NSK Ltd. SATO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2003168107A external-priority patent/JP2005003121A/ja
Priority claimed from JP2003291258A external-priority patent/JP2005061495A/ja
Application filed by NSK Ltd filed Critical NSK Ltd
Publication of EP1632685A1 publication Critical patent/EP1632685A1/de
Publication of EP1632685A4 publication Critical patent/EP1632685A4/de
Application granted granted Critical
Publication of EP1632685B1 publication Critical patent/EP1632685B1/de
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/225—Details of the ribs supporting the end of the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/50—Crowning, e.g. crowning height or crowning radius

Definitions

  • the present invention relates to a cylindrical roller bearing which is used for the transmission etc. of an automobile and durable of an excessive axial load applied thereto, and in particular relates to the improvement of a cylindrical roller bearing which seizure resistance is improved so as not to cause the seizure immediately even in a case of a high-speed rotation or a case of using low-viscosity oil or a case where a lubricating oil device is failed and lubricating oil can not be supplied sufficiently.
  • a cylindrical roller bearing is configured in a manner that, in order to guide cylindrical rollers in the circumferential direction of a raceway ring, a flange portion is provided at the end portion of the raceway ring, and the end face of each of the rollers is made in slide contact with a roller guide-surface formed at the inner surface of the flange portion.
  • a cylindrical roller bearing used for the transmission etc. of an automobile may be used in a state of being applied with an axial load in addition to a radial load.
  • the end face of the roller or the roller guide-surface of the flange portion is slightly tapered or crowned so as not to cause a large edge load.
  • roller bearing in which the surface roughness of the end face of a roller and the flange portion to be contacted to each other is improved thereby to prevent the lubrication failure (see Japanese Patent Unexamined Publication No. JP-A-7-42746 , for example). Further, there is known another roller bearing in which a working grain is provided in a direction almost perpendicular to the relative movement direction in order to improve the lubrication efficiency (see Japanese Patent Unexamined Publication No. JP-A-7-91452 , for example).
  • roller bearing in which minute recess portions are provided at the contact region of a flange portion contacting with the end face of a roller thereby to intend to maintain the forming of an oil film (see Japanese Patent Unexamined Publication No. JP-A-6-241235 , for example). Furthermore, there is known still another roller bearing in which, in order to reduce an amount of heat generated by the sliding operation, the shape of a roller is changed so that the position where the roller contacts with a flange portion is made same as the outer diameter surface of the roller (see Japanese Patent Unexamined Publication No. JP-A-9-236131 , for example).
  • the cylindrical roller bearing disclosed in JP-A-2002-181053 is configured in a manner that the flange surface is crowned or that the contact portion between the inner ring flange portion and the roller end face becomes a contact portion between the outer diameter surface (inner ring flange surface) of a cone having a point as an apex and the spherical surface (the end face of the roller) .
  • the direction of the major axis of the contact ellipse caused at the contact portion between the roller and the flange portion is the radial direction of the inner ring of the bearing.
  • the contact ellipse may protrude from the relief groove of the inner ring flange surfaced or the outer diameter of the flange surface depending on an amount of the axial load, so that an edge load is generated at the boundary surface between the contact ellipse and the relief groove or the boundary surface between the contact ellipse and the outer diameter portion of the flange portion.
  • an object of the invention is to provide a cylindrical roller bearing which can improve a seizure property and improve an allowable rotation speed without increasing the size of a bearing.
  • the surface roughness of 0.15 ⁇ mRa or less can be satisfied by subjecting the raceway surface and the end face of the cylindrical roller to the relieved end grinding.
  • Fig. 1 is a sectional diagram showing a part of the cylindrical roller bearing according to the embodimentofthe present invention .
  • Fig. 2 is an enlarged diagram of a main part showing a portion where the roller guide-surface of a flange portion contacts with the end face of the cylindrical roller.
  • the cylindrical roller bearing 1 includes an inner ring 2, an outer ring 3, cylindrical rollers 4 and a retainer 5.
  • the inner ring 2 includes an inner ring raceway surface 2a at the center portion of the outer peripheral surface thereof.
  • the outer ring 3 includes an outer ring raceway surface 3a at the center portion of the inner peripheral surface thereof.
  • the cylindrical rollers 4 held with a predetermined interval along the circumferential direction by the retainer 5 are disposed so as to rotate freely between the inner ring raceway surface 2a and the outer ring raceway surface 3a.
  • a flange portion 6 for guiding the cylindrical rollers 4 in the circumferential direction of the inner ring 2 and the outer ring 3 is provided at each of the one end of the inner ring 2 and the both ends of the outer ring 3.
  • the flange portion 6 is provided at the inner side surface thereof with a roller guide-surface 7 which contacts with and guides the end faces 4a of the cylindrical rollers 4.
  • the roller guide-surface 7 is formed so as to be opened outside by a predetermined flange open angle ⁇ with respect to the surface perpendicular to the axial direction of the cylindrical roller 4.
  • the cylindrical roller 4 rolls on the inner ring raceway surface 2a while the end face 4a thereof slidably contacts with the roller guide-surface 7 of the flange portion 6.
  • the end face 4a of the cylindrical roller 4 away from the center axis CL of the cylindrical roller 4 by 0.40Da in the radial direction is set as a first position A
  • the end face 4a of the cylindrical roller 4 away from the center axis CL of the cylindrical roller 4 by 0.35Da in the radial direction is set as a second position B
  • the end face 4a of the cylindrical roller 4 is formed so as to contact with the roller guide-surface 7 of the flange portion 6 between the first position A and the second position B.
  • the end face 4a of the cylindrical roller 4 is provided with a convex-shaped crowning portion 4b which is formed by a continuous curve of a curvature radius R passing two points of the first position A and the second position B.
  • an inclined angle ⁇ formed between a straight line connecting the first position A and the second position B and a straight line perpendicular to the center axis CL of the cylindrical roller is set to be 0.5° or less as shown by the following formula.
  • ⁇ tan - 1 a drop amount of the roller at the first position A - a drop amount of the roller at the second position B / 0.05 ⁇ Da ⁇ 0.5 ⁇ ° .
  • the crowning portion 4b of the end face 4a thus formed is given by the relieved end grinding using an elastic grinding stone with the Young's modulus in a range of 10 to 500 MPa.
  • the surface roughness of at least the crowning portion 4b at the end face 4a of the cylindrical roller 4 is set in a range of 0.02 to 0.15 ⁇ mRa.
  • the end face 4a of the cylindrical roller is provided with a circular recess portion 4c at the center portion thereof and a chamfer portion 4d at a portion adjacent to the rolling surface.
  • a region between the first position A and the second position B on the end face 4a of the cylindrical roller 4 is set as a contact region where the roller guide-surface 7 of the flange portion 6 contacts with the end face 4a of the cylindrical roller 4, the contact region opposes to almost the center portion in the thickness direction of the flange portion and so is located at the optimum position for pivotally supporting an axial withstand load.
  • the crowning portion 4b of the end face 4a of the cylindrical roller 4 is configured so as to be formed by the continuous curve which passes the two points of the first and second positions A and B and have the inclined angle ⁇ of 0.5° or less, whereby the contact surface pressure at the contact region in the case of acting an axial load thereon can be reduced and a PV value can be reduced.
  • the inclined angle ⁇ at the contact region of the end face 4a of the cylindrical roller 4 is set to be smaller as compared with the flange open angle ⁇ of the roller guide-surface 7 so that the contact surface pressure is adjusted to be reduced depending on the relation between the inclined angle ⁇ and the flange open angle ⁇ .
  • a crowing portion is not provided at the entirety of the end face of the roller unlike the conventional technique, but only the region between the first position A and the second position B on the end face 4a of the cylindrical roller 4 is formed by the continuous curve, so that the processing time can be made short and the cost can be reduced. Furthermore, since only such the region is processed, the roughness thereof can be made good and the seizure resistance can be improved.
  • the crowning portion 4b may be formed only at the region at least between the first position A and the second position B, or may be formed so as to extend to both sides from the region between the two points A and B.
  • the flange portion on the outer ring side can be configured in the same manner.
  • the flange portion is not limited to one which is directly formed in a flange-shape with respect to each of the inner and outer rings, but the flange portion may be one which is formed by a flange ring provided separately from the raceway ring.
  • the flange portion may be a double flange type or a single flange type. That is, if an axial load is applied to only one direction at the time of usage, the flange portion may be provided only at one end portion side to which the axial load acts. For example, as shown in Fig.
  • a flange ring 10 formed separately from the tack ring may be provided at the inner ring 2, and the roller guide-surface 7 of the flange ring 10 and the end face 4a of the cylindrical roller 4 may be configured in the aforesaid manner.
  • the contact region includes one in a case where at least the center of the contact ellipse caused when the cylindrical roller 4 contacts with the flange portion 6 locates between the first position A and the second position B.
  • each of the cylindrical roller bearings 1 employed in embodiments 1 to 3 and comparative examples 1, 2 had an inner diameter of 45 mm, an outer diameter of 75 mm and a width of 20 mm.
  • Each of the cylindrical rollers 4 had a diameter Da of 7.5 mm and a length of 13 mm.
  • the numbers of the rollers was 18.
  • a retainer made of iron was used as the retainer 5.
  • the flange open angle ⁇ of the flange portion 6 provided at each of the inner ring 2 and the outer ring 3 was set to be 0.5°.
  • the surface roughness of each of the inner ring raceway surface 2a, the outer ring raceway surface 3a and the roller guide-surface 7 of the flange portion 6 was set to a range of 0.05 to 0.20 ⁇ mRa.
  • the surface roughness of the rolling surface of each of the cylindrical rollers 4 of the respective embodiments and the respective comparative examples was set to 0.15 ⁇ mRa.
  • the surface roughnesses of the end faces 4a of the cylindrical rollers 4 of the respective embodiments and the respective comparative examples were set to values shown in a table 1 due to the grinding process using the elastic grinding stone with the Young's modulus in a range of 10 to 500 MPa.
  • the continuity and the drop amounts thereof can be recognized at the respective positions as shown in Fig. 4 by setting the longitudinal magnification and the vertical magnification thereof to about 1000 and about 20, respectively, by using a shape measurement equipment of a longitudinal type, for example.
  • the roller drop amount at the first position A that is, a position away from the roller center axis in the radial direction by 0.40 Da (a position away from the roller center by 3 mm) can be given by calculating the average value of roller drop amounts d1, d1' at two positions obtained from Fig. 4 .
  • the roller drop amount at the second position B that is, a position away from the roller center axis in the radial direction by 0.35 Da (a position away from the roller center by 2.625 mm) can be given by calculating the average value of roller drop amounts d2, d2' at two positions obtained from Fig. 4 .
  • the table 1 shows the average roller drop amounts at the first position A and the second position B and the inclined angles ⁇ given by the average roller drop amounts of the two positions A and B in the respective embodiments and the respective comparative examples.
  • the comparative example 1 is a case where the end face of the cylinder roller was not subjected to the crowing processing.
  • Fig. 5 shows the results of the rotation evaluation test in the respective embodiments and the respective comparative examples.
  • the embodiments 1 to 3 could obtain sufficient allowable rotation speeds as compared with the comparative examples 1, 2. That is, the allowable rotation speeds could be improved since the crowning portion 4b formed by the continuous curve was provided between the first position A and the second position B in the contact region and the inclined angle ⁇ of the straight line connecting the first position A and the second position B was set to be 0.5° or less which was smaller than the flange open angle ⁇ .
  • the surface roughness of the end face 4a including at least the crowning portion 4b was set in a range of 0.02 to 0.15 ⁇ mRa, it became possible to reduce the friction coefficient between the roller guide-surface 7 of the flange portion 6 and the end face 4a of the cylindrical roller 4, and further the oil film forming property was improved and the allowable rotation speed was increased.
  • the surface roughness of the end face 4a was set to 0.05 ⁇ mRa, it became possible to reduce a heat value generated between the flange portion 6 and the end face 4a of the cylindrical roller 4 and so the allowable rotation speed was increased.
  • the cylindrical roller bearing of the first embodiment supposing that the diameter of the cylindrical roller 4 is Da, the end face 4a of the cylindrical roller away from the center axis of the cylindrical roller by 0.40Da in the radial direction is set as the first position A, and the end face 4a of the cylindrical roller away from the center axis of the cylindrical roller by 0.35Da in the radial direction is set as the second position B, the cylindrical roller bearing is configured in a manner that the end face 4a of the cylindrical roller contacts with the roller guide-surface 7 of the flange portion between the first position A and the second position B, the end face 4a of the cylindrical roller has the convex-shaped crowning portion 4b formed by the continuous curve passing the first position A and the second position B, and the angle ⁇ formed between the straight line connecting the first position A and the second position B and the straight line perpendicular to the center axis of the cylindrical roller is set to be 0.5° or less.
  • the contact surface pressure of the contact portion between the roller guide-surface of the flange portion and the end face of the roller can be reduced and the PV value (a product of the bearing surface pressure P and the slip velocity V) canbe reduced, whereby the seizure can be prevented from occurring.
  • the seizure resistance can be improved and the allowable rotation speed can be improved.
  • Fig. 6 is a sectional diagram showing a part of the cylindrical roller bearing according to the exemplary embodiment.
  • Fig. 7 is an enlarged diagram of a main part showing the roller guide-surface of the flange portion and the end face of the cylindrical roller in a state where no load is acting in the cylindrical roller bearing of Fig. 6 .
  • Fig. 8 is an enlarged diagram of a main part showing the roller guide-surface of the flange portion and the end face of the cylindrical roller in a state where a load is acting in the cylindrical roller bearing of Fig. 6 .
  • the cylindrical roller bearing shown in Fig. 6 is a cylindrical roller bearing for a manual transmission for a truck to which a large axial load together with a radial load is applied.
  • the cylindrical roller bearing 21 includes an inner ring 22, an outer ring 23 and cylindrical rollers 24.
  • the inner ring 22 includes, at the outer peripheral surface thereof, an inner ring raceway surface 22a extending from one end thereof along the axial direction.
  • the outer ring 23 includes an outer ring raceway surface 23a at the center portion of the inner peripheral surface thereof. Cylindrical rollers 24 are disposed so as to rotate freely between the inner ring raceway surface 22a and the outer ring raceway surface 23a.
  • a flange portion 25 for guiding the cylindrical rollers 24 in the circumferential direction of the inner ring 22 and the outer ring 23 is provided at each of the other end of the inner ring 22 and the both ends of the outer ring 23.
  • An annual flange ring 26 having an outer diameter larger than that of the inner ring raceway surface 22a is abutted against the one end surface of the inner ring 22.
  • Each of the flange portion 25 and the flange ring 26 is provided at the inner surface thereof with a roller guide-surface 27 which has a flange height L from the outer ring raceway surface or the inner ring raceway surface to the peripheral surface thereof and contacts with and guides the end face 24a of the cylindrical roller 24. As shown in Fig.
  • the roller guide-surface 27 is formed so as to be opened outside by a predetermined flange open angle ⁇ with respect to the surface perpendicular to the axial direction of the cylindrical roller 24.
  • the cylindrical roller 24 rolls on the inner ring raceway surface 22a while the end face 24a thereof slidably contacts with the roller guide-surface 27 of the flange portion 25.
  • the end face 24a of the cylindrical roller 24 is provided at the center portion thereof with a circular recess portion 24b and also provided at a portion adjacent to the rolling surface with a chamfer portion 24c.
  • the end face 24a of the cylindrical roller 24 is provided at the outside (the upper side in Fig. 7 ) of the radial direction of the chamfer portion 24c with a convex-shaped crowning portion 24d formed by a continuous curve with a curvature radius R'.
  • the position of the cross point Q in a state where no load acts is set on the lower side of the flange portion 25 in advance so that the end face 24a of the cylindrical roller 24 actually contacts with almost center position of the roller guide-surface 27 or the lower side from the center position thereof when a large axial load acts.
  • the radial direction distance h of the cross point Q is set in the following manner. 0.05 mm ⁇ h ⁇ 0.5 mm
  • the conventional technique is designed in a manner that the contact point between the end face 24a of the cylindrical roller 24 and the roller guide-surface 27 in a state where no load acts is set at almost the center portion of a flange height L, and a contact ellipse which becomes large when an axial load becomes large is received at the center portion of the flange height L.
  • the contact ellipse protrudes outside of the flange height L and so a PV value becomes large, whereby the seizure likely occurs.
  • the curvature radius R' of the crowning portion 24d is set large with respect to the conventional relation between the curvature radius R' of the crowning portion 24d of the end face and the flange portion 25 and then a calculation is made in view of the influence of the tilt and a skew.
  • the cylindrical roller bearing is configured in a manner that the contact point Q is set on the lower side (the relief groove 28 of the inner ring raceway surface 22a) of the flange portion 25 when an axial load is small and the contact point Q shifts around the center of the flange height L when an actual axial load (for example, 1 ton or more) is applied.
  • the cross point Q when the cross point Q is set so as to satisfy the formula (2) in the state where no load acts, the cross point Q faces within the relief groove 28 which is provided on the inner side (the lower side in Fig. 7 ) of the radial direction from the roller guide-surface 27.
  • the cross point Q may actually contact with the roller guide-surface 27 in a state where no load acts.
  • a ratio between the radial direction distance h and the flange height L of the cross point Q in the state where no load acts is set in the following manner so that the cross point Q does not exceed the flange height L. 0.01 mm ⁇ h / L ⁇ 0.13 mm
  • the cross point Q between the end face 24a of the cylindrical roller 24 and the phantom line C along the roller guide-surface 27 of the flange portion 25 in the state where no load acts is set on the lower side of the flange portion 25, that is, set so that the radial direction distance h of the cross point Q satisfies the formula (2).
  • the cross point Q generates the contact ellipse at almost the center of the flange height L or the lower side position from the center thereof and so actually contacts with the roller guide-surface 27.
  • the PV value at the contact point can be reduced and so the seizure resistance can be improved.
  • the flange portion on the outer ring side can be configured in the same manner.
  • this embodiment may be constituted by the configuration of a roller guide-surface formed at a flange ring provided separately from the raceway ring and the end face of the cylindrical roller.
  • the flange portion may be a double flange type or a single flange type. That is, if an axial load is applied to only one direction at the time of usage, the flange portion may be provided only at one end portion side to which the axial load acts.
  • the seizure efficiency can be further improved by stetting the surface roughness of the raceway surface and the end face of the cylindrical roller to 0.15 ⁇ mRa or less by means of the grinding process and by setting the surface roughness of the end face of the roller and the contact surface of the flange surface to about 0.02 ⁇ mRa by the super finishing
  • each of the cylindrical roller bearings 21 employed in embodiments 4 to 6 and comparative examples 3, 4 was JIS No. NUPK313 (a keystone type having an inner diameter of 65 mm, an outer diameter of 140 mm, a width of 33 mm, a roller diameter Da of 20 mm, a roller length 1 of 23 mm, the number of the rollers of 16 and having no retainer) .
  • the surface roughness of each of the inner ring raceway surface 22a, the outer ring raceway surface 23a and the roller guide-surface 28 of the flange portion 27 was set in a range of 0.05 to 0.20 ⁇ mRa by the relieved end grinding or the super finishing processing. Further, the surface roughness of the rolling surface of the cylindrical roller 24 in each of the embodiments and the comparative examples was set to the same value of 0.15 ⁇ mRa.
  • a table 2 shows the flange open angles ⁇ of the roller guide-surfaces 27and the curvature radiuses R' at the crowning portions 24d of the end faces 24a of the cylindrical rollers 24.
  • the number N of the test was 2, and the rotation speed at which the temperature of the bearing increased to 160 C° or more or at which the bearing vibration became five times as large as the initial vibration due to the abrasion or seizure was set as the allowable rotation speed.
  • Fig. 9 shows the result of the rotation evaluation test in the respective embodiments and the respective comparative examples. As shown in the test results, it was admitted that the allowable rotation speeds in the embodiments 4 to 6 increased sufficiently as compared with the comparative examples 3, 4.
  • the cross point Q in the state where no load acted was the contact point at which the cross point actually contacted with the roller guide-surface 27 and which was almost the center point of the flange height L.
  • the comparative example 4 was specified in a manner that there was scarcely any crowing at the end face 24a, and so the end face 24a of the cylindrical roller 24 contacted with the edge at the relief groove 28.
  • the seizure resistance can be improved by subject the carburizing treatment and the carbonitriding treatment to the cylindrical roller and the inner and outer rings. Further, the seizure resistance can be further improved by using case-hardened steel as the material, setting the retained austenite amount in a range of 20 to 45% and setting the surface hardness Hv in a range of 700 to 850.
  • the retainer used in the embodiments may be a pressed retainer made of iron, a retainer made of plastics or a keystone type having no retainer etc., for example.
  • a pressed retainer made of iron is used or if a retainer made of plastics is used in a high-speed rotation state, the frictional coefficients of the cylindrical roller and the retainer are reduced, whereby the seizure efficiency can be further improved.
  • the invention is usable as the cylindrical roller bearing which can improve the seizure resistance and also improve the allowable rotation speed without increasing the size of the bearing.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Claims (2)

  1. Zylinderrollenlager (1, 21), das einen Innenring (2, 22) mit einer Innenring-Laufbahnfläche (2a, 22a), einen Außenring (3, 23) mit einer Außenring-Laufbahnfläche (3a, 23a) sowie Zylinderrollen (4, 24) umfasst, die jeweils zwischen der Innenring-Laufbahnfläche (2a, 22a) und der Außenring-Laufbahnfläche (3a, 23a) angeordnet sind, wobei der Innenring (2, 22) oder/und der Außenring (3, 23) einen Flanschabschnitt (6, 25) hat/haben, der mit einer Rollen-Führungsfläche (7, 27) versehen ist, die mit Abschlussflächen (4a, 24a) der Zylinderrollen (4, 24) in Kontakt kommt und sie führt, und das Zylinderrollenlager (1, 21) dadurch gekennzeichnet ist, dass
    die Abschlussfläche (4a, 24a) der Zylinderrolle (4, 24) mit der Rollen-Führungsfläche (7, 27) des Flanschabschnitts (6, 25) zwischen einer ersten Position (A) und einer zweiten Position (B) in Kontakt kommt, wobei die erste Position (A) einer Position der Abschlussfläche (4a, 24a) der Zylinderrolle (4, 24) entspricht, die um einen Abstand von 0,40 x Da von der Mittelachse (CL) der Zylinderrolle (4, 24) entfernt ist, wobei Da ein Durchmesser der Zylinderrolle (4, 24) ist, und die zweite Position (B) einer Position der Abschlussfläche (4a, 24a) der Zylinderrolle (4, 24) entspricht, die um einen Abstand von 0,35 x Da von der Mittelachse (CL) der Zylinderrolle (4, 24) entfernt ist,
    die Abschlussfläche (4a, 24a) der Zylinderrolle (4, 24) einen konvex geformten Wölbungsabschnitt (4b, 24d) hat, der von einer durchgehenden Kurve gebildet wird, die die erste Position (A) und die zweite Position (B) durchläuft, und
    ein Winkel α, der zwischen einer geraden Linie, die die erste Position (A) und die zweite Position (B) verbindet, und einer geraden Linie senkrecht zu der Mittelachse (CL) der Zylinderrolle (4, 24) gebildet wird, auf 0,5° oder weniger festgelegt ist.
  2. Zylinderrollenlager (1, 21) nach Anspruch 1, dadurch gekennzeichnet, dass der Winkel α eine Beziehung α < θ in Bezug auf einen offenen Winkel θ der Rollen-Führungsfläche (7, 27) erfüllt und eine Oberflächenrauigkeit wenigstens des Wölbungsabschnitts (4b, 24d) an der Abschlussfläche (4a, 24a) der Zylinderrolle (4, 24) in einem Bereich von 0,02 bis 0,15 µm Ra festgelegt ist.
EP04733675.5A 2003-06-12 2004-05-18 Zylindrisches rollenlager Expired - Fee Related EP1632685B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003168107A JP2005003121A (ja) 2003-06-12 2003-06-12 円筒ころ軸受
JP2003291258A JP2005061495A (ja) 2003-08-11 2003-08-11 円筒ころ軸受
PCT/JP2004/007044 WO2004111477A1 (ja) 2003-06-12 2004-05-18 円筒ころ軸受

Publications (3)

Publication Number Publication Date
EP1632685A1 EP1632685A1 (de) 2006-03-08
EP1632685A4 EP1632685A4 (de) 2012-03-07
EP1632685B1 true EP1632685B1 (de) 2013-07-10

Family

ID=33554398

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04733675.5A Expired - Fee Related EP1632685B1 (de) 2003-06-12 2004-05-18 Zylindrisches rollenlager

Country Status (3)

Country Link
US (1) US7416346B2 (de)
EP (1) EP1632685B1 (de)
WO (1) WO2004111477A1 (de)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7178004B2 (en) 2003-01-31 2007-02-13 Yan Polansky Memory array programming circuit and a method for using the circuit
CN100425850C (zh) * 2003-09-16 2008-10-15 Ntn株式会社 壳式滚针轴承、压缩机主轴的支持结构及活塞泵驱动部的支持结构
US7638850B2 (en) 2004-10-14 2009-12-29 Saifun Semiconductors Ltd. Non-volatile memory structure and method of fabrication
DE112006000523B4 (de) * 2005-03-03 2017-03-02 Nsk Ltd. Axial-Zylinderrollenlager
DE102005061103A1 (de) * 2005-12-21 2007-07-05 Schaeffler Kg Wälzlager mit verbesserter Bordgeometrie
DE102005061102A1 (de) * 2005-12-21 2007-07-05 Schaeffler Kg Wälzlager
US7760554B2 (en) 2006-02-21 2010-07-20 Saifun Semiconductors Ltd. NROM non-volatile memory and mode of operation
DE102008028164B4 (de) * 2008-06-12 2021-07-01 Ab Skf Rolle und Rollenlager mit der Rolle
JP5455329B2 (ja) * 2008-06-24 2014-03-26 Ｎｔｎ株式会社 円筒ころ軸受
DE102008025595A1 (de) * 2008-06-27 2009-12-31 Schaeffler Kg Lager, insbesondere Radsatzlager, speziell Radsatzlager für Bahnräder
JP5182068B2 (ja) * 2008-12-24 2013-04-10 株式会社ジェイテクト 転がり軸受
DE102010018553A1 (de) * 2010-04-28 2012-01-19 Aktiebolaget Skf Rolle und Rollenlager
US9702407B2 (en) * 2010-11-16 2017-07-11 Harnischfeger Technologies, Inc. Roller circle assembly for heavy machinery
DE102011076328B4 (de) * 2011-05-24 2013-11-07 Aktiebolaget Skf Geometriekonzept für einen Bord eines Rollenlagers
JP2013117249A (ja) * 2011-12-02 2013-06-13 Ntn Corp ころ軸受
CN103998798A (zh) * 2011-12-13 2014-08-20 美国光洋轴承有限责任公司 轴承外环
FR2998630B1 (fr) * 2012-11-28 2015-02-20 Ntn Snr Roulements Palier a roulement
JPWO2015076271A1 (ja) * 2013-11-21 2017-03-16 日本精工株式会社 円筒ころ軸受及びトランスミッション用軸受装置
JP6323136B2 (ja) * 2014-04-16 2018-05-16 株式会社ジェイテクト ころ軸受用軌道輪、ころ軸受及び動力伝達装置
WO2016040821A1 (en) 2014-09-11 2016-03-17 Koyo Bearings North America Llc Axle wheel end axial thrust assembly
CN108603530A (zh) 2016-01-21 2018-09-28 Ntn株式会社 滚动轴承、滚动装置以及滚动装置的制造方法
EP3615821B1 (de) * 2017-04-26 2022-07-27 The Timken Company Nichtelliptisches kontaktprofil für ein rollenlager
US10883542B2 (en) * 2019-05-21 2021-01-05 Raytheon Technologies Corporation Cylindrical roller bearing containing a crowned inner ring shoulder
DE102020211036B4 (de) * 2020-09-02 2022-04-14 Aktiebolaget Skf Anordnung mit einem Schleifwerkzeug und einer Rolle für ein Rollenlager sowie Verfahren zum Herstellen einer Rolle für ein Rollenlager

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5436990Y2 (de) 1975-06-09 1979-11-07
US4027930A (en) * 1975-12-19 1977-06-07 The Garrett Corporation Bearing assembly and method
JPS5843609A (ja) * 1981-09-09 1983-03-14 Toshiba Corp 弾性表面波装置
JPS59106719A (ja) * 1982-12-08 1984-06-20 Koyo Seiko Co Ltd 円筒ころ軸受
JPH06241235A (ja) 1993-02-17 1994-08-30 Koyo Seiko Co Ltd ころ軸受
JPH0712119A (ja) * 1993-06-28 1995-01-17 Nippon Seiko Kk 円筒ころ軸受
JPH0742746A (ja) 1993-07-30 1995-02-10 Ntn Corp ころ軸受
JPH0791452A (ja) 1993-07-30 1995-04-04 Ntn Corp 転がり軸受
JP3511782B2 (ja) 1996-02-27 2004-03-29 日本精工株式会社 転がり軸受
JPH09236131A (ja) 1996-02-29 1997-09-09 Ntn Corp ころ軸受
JPH10196660A (ja) 1996-11-13 1998-07-31 Nippon Seiko Kk ころ軸受
US6086261A (en) * 1998-01-14 2000-07-11 Ntn Corporation Tapered roller bearing
JPH11236920A (ja) * 1998-02-24 1999-08-31 Nippon Seiko Kk 転がり軸受
JP2000065066A (ja) * 1998-08-19 2000-03-03 Nippon Seiko Kk 円筒ころ軸受
JP2002181053A (ja) * 2000-12-13 2002-06-26 Nsk Ltd ころ軸受
JP2003021145A (ja) * 2001-07-05 2003-01-24 Nsk Ltd ころ軸受
CN1260484C (zh) * 2001-11-06 2006-06-21 日本精工株式会社 径向滚子轴承
TWI285243B (en) * 2002-03-20 2007-08-11 Ntn Toyo Bearing Co Ltd Cylindrical roller bearing

Also Published As

Publication number Publication date
EP1632685A4 (de) 2012-03-07
WO2004111477A1 (ja) 2004-12-23
US7416346B2 (en) 2008-08-26
US20060126983A1 (en) 2006-06-15
EP1632685A1 (de) 2006-03-08

Similar Documents

Publication Publication Date Title
EP1632685B1 (de) Zylindrisches rollenlager
US6328477B1 (en) Tapered roller bearings and gear shaft support devices
EP1770294B1 (de) Verjüngtes Rollenlager
EP1231410B1 (de) Rollenwälzlager und die Rollenwälzlager aufweisende Kette
EP2952763B1 (de) Kugellager mit mehrpunktkontakt
US5890815A (en) Roller bearing
US20070269158A1 (en) Tapered roller bearing for automobile transmission
US5456538A (en) Roller bearing
US20070116393A1 (en) Needle roller bearing, crank shaft supporting structure, and split method of outer ring of needle roller bearing
US20050041901A1 (en) Roller bearing and double row cylindrical roller bearing
EP3584459A1 (de) Kegelrollenlager
US10890213B2 (en) Tapered roller bearing
EP1647727A2 (de) Kegelrollenlager
US20210025446A1 (en) Tapered roller bearing
US20040240764A1 (en) Roller bearing
EP1795770B1 (de) Zylindrisches kugellager
JP2005106234A (ja) 円錐ころ軸受と円錐ころ加工方法
EP3690265B1 (de) Kegelförmiges kugellager
JP2005003121A (ja) 円筒ころ軸受
EP1967703B1 (de) Verriegelungsarm, verriegelungsbolzen, ventilkappe, einstellschraube, gelenkaufnahmeglied und ventil einer armartigen ventilbetriebsvorrichtung
JPH0791452A (ja) 転がり軸受
US7435007B2 (en) Self-aligning roller bearing
JP2005061495A (ja) 円筒ころ軸受
JPH07103243A (ja) 転がり軸受
JP4075364B2 (ja) 円筒ころ軸受

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20051212

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE GB

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE GB

A4 Supplementary search report drawn up and despatched

Effective date: 20120202

RIC1 Information provided on ipc code assigned before grant

Ipc: F16C 33/58 20060101ALI20120127BHEP

Ipc: F16C 19/26 20060101ALI20120127BHEP

Ipc: F16C 33/60 20060101ALI20120127BHEP

Ipc: F16C 33/34 20060101AFI20120127BHEP

17Q First examination report despatched

Effective date: 20120730

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F16C 33/34 20060101AFI20121206BHEP

Ipc: F16C 33/58 20060101ALI20121206BHEP

Ipc: F16C 19/26 20060101ALI20121206BHEP

Ipc: F16C 33/60 20060101ALI20121206BHEP

Ipc: F16C 19/22 20060101ALI20121206BHEP

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602004042672

Country of ref document: DE

Effective date: 20130905

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20140411

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602004042672

Country of ref document: DE

Effective date: 20140411

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20170517

Year of fee payment: 14

Ref country code: DE

Payment date: 20170509

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602004042672

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180518

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181201

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180518